Reversible rotary hydraulic coupling



J y 3, 1954 w. E. LEWIS 2,683,351

REVERSIBLE ROTARY HYDRAULIC COL JPLING Filed Aug. 7, 1952 s Sheets-Sheet 1 //2 I I Warren E. Lew/s mmvroze.

BY @Mm REVERSIBLE ROTARY HYDRAULIC COUPLING Filed Aug. 7, 1952 5 Sheets-Sheet 2 Warren E. Lewis I68 INVEN TOR.

IL A; 2/6 WWW July 13, 1954 w. E. LEWIS 2,533,351

REVERSIBLE ROTARY HYDRAULIC COUPLING Filed Aug. 7, 1952 .3 Sh ts-Sheet 5 Warren E. Lewis INVENTOR.

BY WW 8M Patented July 13, 1954 OFFICE REVERSIBLE ROTARY HYDRAULIC COUPLING Warren E. Lewis, Kankakee, Ill.

Application August 7, 1952, Serial No. 303,090

Claims.

This invention relates in general to improvements in fluid transmissions and is an improvement on the fluid transmission set forth in my co-pending application, Serial No. 167,604, filed June 12, 1950.

The primary object of this invention is to provide an improved fluid transmission which includes a shiftable turbine member whereby the speed and power of the turbine member may be varied as desired with respect to a drive impeller of the transmission.

Another object of this invention is to provide an improved fluid transmission which may be connectedbetween a power source and a drive shaft to provide a vibrationless flow of power through controllable hydraulic means with means for selectively reversing the flow of power and varying the speed and power of the unit as desired.

Another object of this invention is to provide an improved fluid transmission which is of a relatively simple and compact design whereby the same may be utilized as a replacement for existing fluid transmissions of vehicles now on the market.

A further object of this invention is to provide an improved fluid transmission which includes a rotating reversing vane for selectively reversing the flow of hydraulic fluid of the transmission whereby the direction of rotation of a turbine member may be selectively reversed, said reversing vane being mounted for independent rotation and bein provided with brake means for actively engaging the same.

A still further object of this invention is to provide improved control means for a fluid transmission, said control means including a shift mechanism for axially shifting a turbine member for moving the same from a forward drive position to a reverse drive position, and brake means for selectively positioning a reversing vane for cooperation with said turbine member.

With these objects definitely in view, this invention resides in certain novel features of construction, combination and arrangement of elements and portions as will be hereinafter described in detail in the specification, particularly pointed out in the appended claims, and illustrated in the accompanying drawings which form transmission being in a position for forward drive;

Figure 2 is a fragmentary transverse vertical sectional view taken substantially upon the plane indicated by the section line 2-2 of Figure 1 and shows the general construction of the blading of the transmission;

Figure 3 is a fragmentary longitudinal horizontal sectional View similar to Figure 2 and shows the arrangement of the vanes when the transmission is in position for reverse rotation;

Figure 4 is a fragmentary horizontal sectional view taken through the rear portion of the fluid transmission of Figure 1 substantially along the section line 44 and shows the general construction of means for controlling the direction of rotation of the driven shaft by the fluid transmission;

Figure 5 is a fragmentary transverse vertical sectional view taken substantially upon the plane indicated by the section line 5- 5 of Figure 4 and shows the means for controlling movement of brake drums adapted to lock the reversing vane of the fluid transmission in a stationary position;

Figure 6 is an enlarged fragmentary longitudinal vertical sectional view taken substantially upon the plane indicated by the section line 66 of Figure 5 and shows the general construction of cam means for actuating the brake bands of the brake;

Figure 7 is a fragmentary transverse vertical sectional view taken substantially upon the plane indicated by the section line l-l of Figure 4 and shows the connection between a shift yoke and a brake control arm; and

Figure 8 is an enlarged fragmentary vertical sectional View showing the manner in which the brake bands are adjustably mounted.

Similar characters of reference designate similar or identical elements and portions throughout the specification and throughout the different views of the drawings.

Referrin now to the drawings in particular, it will be seen that there is illustrated in Figure 1 the general construction of the fluid transmission, which is the subject of this invention, the fluid transmission including an outer supporting housing which is referred to in general by the reference numeral 10. The supporting housing I0 is adapted to be secured at its forward end to the rear end of a power unit (not shown) and is partially supported thereby. The supporting housing it includes an upper half, which is 16' ferred to in general by the reference numeral i2 and a lower half, which is referred to in general by the reference numeral M, the halves being connected together along a horizontal plane by suitable fastening means I6. The lower half i4 is removable from the upper half 12 in order that access to the interior of the supporting housing it may be obtained for repairing and adjusting the fluid transmission.

The upper half [2 includes a vertical front wall it which has an enlarged circular opening it therethrough, the opening 20 receiving the rear end of a crank shaft 22 of the power unit (not shown).

Secured to the rear end of the crank shaft 22 for rotation therewith is a fly wheel 2t. having starter engaging teeth 2% around the circumference thereof. The fly wheel 24 is secured to a flange 25% on the rear end of the crank shaft 22 by suitable fasteners 30.

The upper half i2 of the supporting housing ii] also includes a rear wall 32 which is in spaced parallel relation to the front wall 18. The rear wall 32 is provided with a circular opening 34 in alignment with the circular opening 20 and in which is mounted a two-piece bearing housing which is referred to in general by the reference numeral 38, The bearing housing 36 includes a forward bearing case 38 which is locked in the opening 3d, and a bearing cap 49 which is removably connected to the bearing case 38 at the rear end thereof by suitable fasteners 42.

The bearing case 38 is provided with a rearwardly open bearing receiving recess 44 in which is positioned a suitable bearing 46. The bearing to is retained within the bearing receiving recess ts by the bearing cap 4B and has rotatably supported therein a driven shaft 38. The driven shaft as extends both forward and rearwardly through the bearing 46 and is provided with a reduced forward end 56 which is rotatably supported within a rearwardly extending centrally located boss 52 on the fly wheel 24. The boss 52 is provided with a centrally located bore in which is mounted a pilot bearing 56, the pilot bearing 55 being in supporting engagement with the reduced forward end E2 of the driven shaft 43.

Mounted on both the boss 52 and the driven shaft '58 for independent rotation is a two-piece casing which is referred to in general by the reference numeral 58. The casing .58 includes a forward reversing vane portion, which is referred to in general by the reference numeral 60, and a rear cover portion, which is referred to in general by the reference numeral 62. The cover portion s2 is connected to the rear edge of the reversing vane portion 60 by suitable fasteners 64 in order that access to the interior of the casing as may be readily attained.

It will be noted that the reversing vane portion Gil includes a front wall 56 which has a rearwardly projecting hub $3. The hub 8 has a bearing receiving recess in the rear face thereof in which is mounted a suitable bearing Hi. The bearing 76 is mounted for rotation on the boss 52 of the fly wheel 25, and supports the forward end of the casing till. The front wall 66 of the reversing vane portion *5!) is also sealed to the boss 52 by a sealing ring 12.

Positioned within the reversing vane portion 60 for rotation with the fly wheel 24 and crank shaft 22 is a drive impeller which is referred to in general by the reference numeral it. The drive impeller it includes a generally circular supporting plate it which has a rearwardly offset central portion 73. The central portion i8 is splined to the boss 52 and retained in splined engagement by a locking element 89 threadedly engaged within the boss 52. The drive impeller 14 also includes a rearwardly extending impeller vane ring 82 which is connected at the outer circumferential edge of the supporting plate 1'4.

Also mounted within the casing 58 for rotation is a turbine member, which is referred to in general by the reference numeral 86. The turbine member 8 includes a backing plate of similar configuration to the backing plate E4, the backing plate being referred to in general by the reference numeral 86 and having a forwardly extending central hub portion 88, The hub portion has integral therewith a rearwardly extending sleeve 90 which is splined to the driven shaft 43 for sliding movement therealong.

The turbine member 84 also includes a vane ring 92 which is positioned forwardly of the supporting plate 36 and is of a circumference greater th an the outer circumference of the impeller vane ring 82. The turbine vane ring 3?. is adapted to be positioned concentrically of the impeller ring 82, as is best illustrated in Figure 1, and is secured to the backing plate 86 by a plurality of circumferentially spaced connecting rods 94, the rear ends of the connecting rod 96 being rigidly connected to the backing plate 85.

It will be noted that the cover portion E2 of the casing c3 also includes a rear wall 96 which has an enlarged hub portion 98. The hub portion 93 is provided with a centrally located forwardly open bearing receiving recess tilt in which is mounted a suitable bearing N12. The bearing we also engages the outer surface of the sleeve 9E: and supports the rear portion of the casing 58. The hub 93 also includes a seal ring ltd which is in engagement with the outer surface of the sleeve iii! for sealing the rear end of the casing 58 against escape of hydraulic fiuid.

It will be noted that the reversing vane portion B ll also includes a reversing vane ring I66 integral with the interior thereof. The reversing vane ring it has an inner circumference substantially equal to the outer circumference of the vane ring 92 and is positioned closely adjacent the same. The reversing vane ring GS is intended to reverse the direction of flow of hydraulic fluid driven by the impeller ring $2 in order that the direction of rotation of the turbine member 34 may be selectively reversed.

Referring once again to Figure 1, it will be seen that mounted on the top surface of the supporting housing 50 is an oil reservoir H8. The oil reservoir it includes a filling opening H0 which is normally closed by removable closure cap H2 and is intended for convenient replacement of oil. The lower end of the oil reservoir 58 includes a tubular projection I l which is externah ly threaded and is threadedly engaged in an internally threaded bore HE; of an upwardly projecting boss i i8 on the outer surface of the supporting housing iii.

Also threadedly engaged in the threaded bore H5 is a fitting iii! to which is connected a top end of a flexible tubing I22. The lower end of the flexible tubing 122 is connected to a second fitting iEil disclosed within the interior of the supporting housing it; and connected to an L-shaped fitting 526. The L-shaped fitting !26 is carried by the forward wall of the bearing case 38 and communicates with a circular oil passage i28 therein. The oil passage i28 communicates with the bearing receiving recess ill and hydraulic fluid from the reservoir 1% lubricates the bearing it. In order that hydraulic fiuid may not escape from the bearing receiving recess 44, the

bearing cap 46 is provided with a centrally located sealing ring I36 which engages the driven shaft 48 in sealing relation at the rear end of the bearing 46. 'The bearing case 38 is also sealed against escape of hydraulic fluid by a sealing ring I32 which also engages the driven shaft 48.

It will be noted that the driven shaft 48 is provided with an axial bore I34 whose rear end communicates with a transverse bore I36. The transverse bore I36 is in alignment with the circular oil passage I28 and is adapted to receive oil from the oil reservoir I68. The forward end of the bore I34 is positioned within the casing 58 between the drive impeller 14 and the driven impeller 84 and communicates with the interior of the casing 58 by a transversely extendin bore In view of the foregoing, it will be readily seen that the casing 58 may be filled with hydraulic fluid at all times due to the filling action of the reservoir I08. In order that the casing 58 may be also conveniently filled and drained, the reversing vane portion 66 is provided with an outwardly projecting boss I46. The boss I46 is provided with an internally threaded bore I42 which is normally closed by a closure element I44.

Referring now to Figures 1 and 4, it is seen that there is provided shift means for shifting the turbine member 84 longitudinally of the driven shaft 48. The shaft means includes a throw out bearing I46 which is mounted on the rear end of the sleeve 96 and secured thereto by a locking element I48. Pivotally connected to the outer race of the bearing I46 by suitable connecting elements I56 are bifurcated end portions I52 of a shifting yoke, which is referred to in general by the reference numeral I54.

The shifting yoke I54 includes an elongated shaft portion I56 which has mounted thereon intermediate its ends a sleeve I56. Pivotally connected to the sleeve I58 by suitable connecting means I6!) is a pair of support arms I62. The rear ends of the support arms I62 are rigidly connected to the front base of the rear wall 3 of the supporting housing ID, the supporting arms I64 forming a fulcrum for the shifting yoke I54.

It will be noted that the shaft I56 extends through an elongated slot I64 in the wall of the upper half I2 of the supporting housin It and is provided with a conventional pedal assembly (not shown) for moving the same.

It will be seen that when the outer end of the shaft I56 is moved forwardly the central portion thereof pivots about the connecting means I60 with the result that the bifurcated inner end of the shift yoke I54 is moved rearwardly with the resultant rearward movement of the turbine member 84.

It will be understood that for certain stages of the hydraulic transmission, which is the subject of this invention, it is desired that the reversing vane ring I65 remains stationary. In order that the reversing vane ring I66 remains stationary, the casing 58 must be locked against rotation within the supporting housing In. In order that the casing s may be selectively locked against rotation, the fluidtransmission also includes a brake mechanism which is referred to in general by the reference numeral I66. The brake mechanism I66 includes a substantially annular brake ring I68 which has secured to the inner surface thereof a substantially circular brake lining I16. As is best illustrated in Figure 8, thebrake ring 6 I68 is supported from the supporting housing I I] by a supporting structure which is referred to in general by the reference numeral I12. The supporting structure I12 includes a channel element which is referred to in general by the reference numeral I14 connected to the outer surface of the brake ring I68. The channel element I14 includes a web I16 which has integral therewith a pair of inwardly directed flanges I18. The flanges I18 terminate in upwardly and downwardly wing flanges I86. The wing flanges 186 are rigidly secured to the outer surface of the brake rin I68.

The supporting structure I12 also includes a plate I82 which is connected to the inner sur face of the supporting housing II) by suitable fasteners I86. Rigidly carried by the plate I62 is a second channel element which is referred to in general by the reference numeral I36. The channel element I86 includes a web I 88 which extends transversely of the web I16 and is positioned between the fianges I 18 of the channel element I 14. Integral with the Web I68 are outwardly extending spaced parallel flanges I96 whose outer ends are connected to the plate I82. It will be noted that the flanges I90 are disposed on opposite sides of the web I16 so that the channel element I14 is prevented from shifting both longitudinally and circumferentially.

Carried by the web I16 and having its end threadedly engaged in the web I88 is an adjusting member I92. Carried by the adjusting member I92 and disposed between the webs I16 and I68 is a coil sprin I96 for maintaining an adjustment set by the adjustin member I92.

It will be readily understood that there are a plurality of supporting constructions I12 spaced circumferentially about the brake ring I68. It will also be understood that the supporting constructions I12 may be easily reached either through special hand holes (not shown) in the supporting housin In or by removing the lower half I4.

Referring now to Figures 5 and 6 in particular, it will be seen that the ends of the brake ring I68 are in spaced relation. Secured to the upper end thereof is an outwardly extending L-shaped member I96 which is of a lesser width than the brake ring I66 and positioned centrally thereof. Also secured to the upper end of the brake ring I68 and projecting outwardly therefrom is a pair of spaced parallel connecting members I66. The connecting members I98 extend downwardly from the upper end of the brake ring I68 on opposite sides of the L-shaped member I96 and is provided with lower threaded stud portions 266. Adjustably mounted on the lower threaded stud portions 266 and extending therebetween is a plate 262, the plate 262 being retained on the threaded stud portions 206 by a suitable nut element 264.

The lower end of the brake ring I68 is of a reduced width and is referred to by the reference numeral 206. The lower end 206 terminates in an outwardly directed flange 268 which is in spaced parallel relation to an outwardly prov,iecting portion of the L-shaped member I96. Extending between and mounted in a socket in the L-shaped element I96 and the flange 268 is a spring 2III which urges the ends of the brake ring I68 apart.

It will be noted that the brake ring I66 is mounted around a cylindrical drum portion 2I2 of the cover portion 62 and the brake lining I16 lies closely adjacent the same when the ends of the brake rings I10 are in their spaced posiassassin- 7; In order that the ends of the brakering l58= maybe urged together, the brake mechanism 166 also includes an actuating mechanism which is referred to in general by thereference-numeral 2M; The actuating mechanism 2M in cludes a shaft 2H5 which passes through a bore will be seen that the cam 222 is disposed between.

the flange 208 and the plate 292 and that rotation of the same will urge the flange 208 away from the plate 2&2. Movement of the flange 208 away from the plate 252 results in the movement of the same towards the L-shaped member I98 with the resultant compressing of the spring. 2m and the tightening of the brake band i'lil against the brake drum portion 2 [2 of the cover portion 82.

Referring now to Figures 4 and '7 in particular, it will be seen that the outer end of the shaft 216 has connected thereto for rotation therewith a shift arm 224. The shift arm 224 has pivotally connected thereto one end of an L-shaped link 226. The other end of the L- shaped link 226 is connected to the shaft I56 by a ring portion 223. When the shaft I56 is moved forwardly to shift the turbine member 84, the shaft 2 i 5 is rotated with the resultant clamping of. the drum portion 2i2 by the brake band Ill]. The clamping of the drum portion 212 results in the locking of the casing 58 against rotation during the movement of the turbine member 84. Although the link 226 has been illustrated and described as being connected to the shaft l56 for actuation thereby, separate actuating means for the link 226 to permit independent operation of the brake mechanism We may beprovided.

Referring now to Figure 1 in particular, it will be seen that the impeller and turbine vane rings of the fluid transmission are in their forward drive position. When in such a position, the turbine vane ring 92 is in vertical alignment and concentric with the drive impeller ring 82.. As the drive impeller ring 82 is rotated hydraulic fluid driven by the same strikes the turbine vane. ring 92 with the resultant rotation of the turbine member $4 and the rotation of the driven shaft 48. Hydraulic passing beyond the turbine vane ring 92 engages the reversing vane ring 106 which reverses the direction of flow of the hydraulic fluid and returns the same towards the center of the mechanism. When so positioned, the reversing vane ring W8 is free to rotate and the fly wheel the drive impeller M, the turbine member iii, the driven shaft and the casing 58 rotate forwardly.

will be seen that as the turbine vane ring 92 is moved rearwardly with respect to the impeller vane ring 82 the force exerted thereon by the impeller vane ring 32 becomesneutralized by the reverse flow of hydraulic fiuidadirected by the reversing vane ring IilB with the result'that when the turbine vane ring 92 is in an intermediate position, no rotary force is exerted thereon and the fluid transmission may be considered-to be in neutral. if necessary, the brake mecha-. nism E56 could be actuated to prevent rotationof the reversing vane ring M61 The arrangement ofthe vanes gives the. drive impeller the advantage or the turbine :member. inasmuch :as, it has a smaller pulling. radius. vIn order that more power may be obtained and-ithe .draulic fluid therethrough during the a minor details from the embodiment of ta; turbinemember 34 be driven at a lower rate, the brake' mechanism I66 may be actuated and the casing58 locked against rotation. The locking of the casingiili against rotation results in the stationary positioning of the reversing vane ring [0.6. Asthe hydraulic fluid circulates through the reversing" vane ring and back into the drive impeller, the reversing vane ring let becomes a reactor and increases the torque and reduces the speed of the turbine member 8 1.

When it .is. desired to rotate the driven shaft 48 and the turbine member M in reverse directions, the turbine member B l is moved rearwardly by utilizing the control mechanism When the turbine member 24 is retained in such a position, thereversing vane ring. Hi5 is locked against, rotation with the result that hydraulic fluid driven by the drive impeller i i has its direction of flow reversed before striking the turbine vane ring 92 and results in a reverse rotation of the turbine member lid. It will be noted that the support plate 86 of the turbine member as is provided with a plurality of circumferentially spaced openings 235: to permit flow of hyshifting operat on.

The fluid transmission, which is the subject of this invention, when intended for use in an. automobile has a forward and reverse pulling torque which is substantially equal to each other and is equivalent to a normal second gear. Therefore, a low gear would be necessary for puiiing, which can be placed in the conventional position, and can be engaged when the fluid tranw mission-lain a neutral position. This arrangement would also give a two speed reverse.

The fluid transmission, which i the of this invention, also a variable speed control,

and would'also be good for industrial i shifting the turbine member 8 the missionycould-be used to give any speer constant speed of a power unit to as; toa reverse speedup to about onespeed of the power unit. This see both adjusting the position of the her and the use of the brake mechan.

The operation of this device will und from the foregoing description the details thereof, taken in connection th above 1 cited objects and-drawings. Furthe' descriptien would appear to be unnecessary.

Minormodificationsof the device, vary as newv is:.

l. Areversible rotaryhydraulic or prising axially fixed drive and mountedfor-rotation relative to c impeller carried by said d ve shefor rotation therewith, a turbine member ca by said drivenshaft for rotation therewith, a rounding. said impeller and said tu 'ie a reversing vane ring carried by sa: reversing the direction of. flow of f by .said impeller, said turbine rr mountedfor axial movement an vane ring selectively positionable 1e path of fluid fiowing-between-said impeller reversing va-ne ring 'andfluid flowing between said reversing vane ring and said impeller to selectivelllii i 9 1y control the direction of rotation of said driven shaft.

2. A reversible rotary hydraulic coupling com prising axially fixed drive and driven shafts mounted for rotation relative to each other, an impeller carried by said drive shaft for rotation therewith, a turbine member carried by said driven shaft for rotation therewith, a casing surrounding said impeller and said turbine member, a reversing vane ring carried by said casing for reversing the direction of flow of fluid circulated by said impeller, said turbine member being mounted for axial movement and including a vane ring selectively positionable in the path of fluid flowing between said impeller and said reversing vane ring and fluid flowing between said reversing vane ring and said impeller to selectively control the direction of rotation of said driven shaft, the vane ring of said turbine memher being carried by a support plate in spaced relation thereto, movement of said support plate varying the effective volume of the fluid flow portion of said casing.

3. A reversible rotary hydraulic coupling com prising axially fixed drive and driven shafts mounted for rotation relative to each other, an impeller carried by said drive shaft for rotation therewith, a turbine member carried by said driven shaft for rotation therewith, a casing surrounding said impeller and said turbine member, a reversing vane ring carried by said casing for reversing the direction of flow of fluid circulated by said impeller, said turbine member being mounted for axial movement and including a vane ring selectively positionable in the path of fluid flowing between said impeller and said reversing vane ring and fluid flowing between said reversing vane ring and said impeller to selectively control the direction of rotation of said driven shaft, said impeller, turbine member and easing being rotatable relative to each other, means for selectively locking said casing against rotation.

4. A reversible rotary hydraulic coupling comprising axially fixed drive and driven shafts mounted for rotation relative to each other, an impeller carried by said drive shaft for rotation therewith, a turbine member carried by said driven shaft for rotation therewith, a casing surrounding said impeller and said turbine member,

a reversing vane ring carried by said casing for reversing the direction of flow of fluid circulated by said impeller, said turbine member being mounted for axial movement and including a vane ring selectively positionable in the path of fluid flowing between said impeller and said reversing vane ring and fluid flowing between said reversing vane ring and said impeller to selec tively control the direction of rotation of said driven shaft, said casing being mounted in a fixed housing, said driven shaft being rotatably journaled in said housing, a fluid reservoir carried by said housing, a fluid passage through said driven shaft continuously communicated with the interior of said casing, a fluid line continuously communicating said fluid reservoir with said fluid passage, said fluid reservoir gravity feeding said casing.

5. A reversible rotary hydraulic coupling comprising axially fixed drive and driven shafts mounted for rotation relative to each other, an impeller carried by said drive shaft for rotation therewith, a turbine member carried by said driven shaft for rotation therewith, a casing surrounding said impeller and said turbine member, a reversing vane ring carried by said casing for reversing the direction of flow of fluid circulated by said impeller, said turbine member being mounted for axial movement and including a vane ring selectively ositionable in the path of fluid flowing between said impeller and said reversing vane ring and fluid flowing between said reversing vane ring and said impeller to selectively control the direction of rotation of said driven shaft, said drive shaft having mounted thereon a flywheel disposed externally of said casing, said casing being restrained against axial movement by said flywheel and said impeller.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 975,795 Radcliffe Nov. 15, 1910 1,298,990 Mason Apr. 1, 1919 2,015,212 Beaumont Sept. 24, 1935 2,352,109 Leary June 20, 1944 2,387,415 Sibert Oct. 23, 1945 2,398,665 Pietsch Apr. 16, 1946 2,534,104 Chiville Dec. 12, 1950 

